ES2525730T3 - Proportional pressure controller - Google Patents

Abstract

A proportional pressure controller (10), comprising: a controller assembly that includes: a body having inlet (28), outlet (30) and exhaust (32) ports; a filling valve (54), in communication with a pressurized fluid in the inlet port; a discharge valve (56) in communication with the pressurized fluid in a discharge passage of the filling valve; an inlet seat valve (36) and an exhaust seat valve (80); an outlet flow passage (34) in communication with the pressurized fluid when the inlet seat valve (36) moves to an open position of the inlet seat valve, the outflow passage communicating (34) with the outlet port (30) and a common exhaust / outlet passage (86) normally isolated from the exhaust port when the exhaust seat valve is in a closed position of the exhaust seat valve; and an inlet and fill passage (62) that provides fluid communication between an inlet flow passage (58) and the fill valve (54), and isolated from each of, the outflow passage passage (34) , the common exhaust / output passage (86) and the output and exhaust ports in all operating conditions of the controller, the entry and filling passage (62) communicating with the entry passage (58) and being continuously pressurized by the pressurized fluid in the inlet passage; and characterized in that it includes a first pressure signaling device (110) adapted to emit a detected pressure signal, placed in the discharge passage downstream of the filling valve (54) to isolate the fluid pressure signaling device in The exit port.

Description

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DESCRIPTION

Proportional pressure controller

This disclosure relates to proportional pressure controllers, adapted for use in pneumatic systems.

This section provides background information related to the present disclosure, which is not necessarily prior art.

Proportional pressure controllers often include main internal valves that move to allow a pressurized fluid to discharge to a drive device, while controlling the operating pressure of the fluid in the drive device. Main valves are commonly relocated using solenoid operators. This configuration increases weight and the expense of the controller, and requires a significant electrical current to relocate the main valves.

Known proportional pressure controllers, as shown in US 4 316 486, are also often susceptible to being below or above the system pressure, in which due to the mass and the operating time of the main valves, the signal to reduce or stop the flow of pressurized fluid to the drive device, may occur too soon or too late, to prevent it from being reached

or the desired operating pressure is exceeded. When this occurs, the control system that operates the solenoid actuators begins a rapid opening and closing sequence, so that the controller "hunts" the desired operating pressure. This rapid operation is known as "motor navigation" and also increases the wear of the controller and the operating costs.

This section provides a general summary of the disclosure and is not an extensive disclosure of its full scope or all its features.

According to several embodiments, a proportional pressure controller includes: a controller assembly that includes a body having inlet, outlet and exhaust ports; a filling valve that is in communication with a pressurized fluid at the inlet port; a discharge valve, which is in communication with the pressurized fluid in a discharge passage of the filling valve; and an inlet seat valve and an exhaust seat valve. An outlet flow passage is in communication with the pressurized fluid when the inlet seat valve is moved to an open position of the inlet seat valve. The passage for outflow communicates with the outlet port and a common exit / exhaust passage normally isolated from the exhaust port when the exhaust seat valve is in a closed position of the exhaust seat valve. A filling inlet passage provides fluid communication between the inlet passage and the filling valve, and is isolated from each of the outflow passage, the common exhaust / outlet passage and the outlet and exhaust ports, in all operating conditions of the controller. The filling inlet passage communicates with the inlet passage and is continuously pressurized by the pressurized fluid in the inlet passage. A pressure sensor is placed in the discharge passage to isolate the fluid pressure sensor at the outlet port.

According to additional embodiments, a proportional pressure controller includes a controller body that includes: inlet, outlet and exhaust ports; an inlet passage and an outlet passage, the inlet passage communicating a flow of pressurized fluid from the inlet port to the outlet passage, and the outgoing passage communicating the flow of pressurized fluid from the inlet passage to the port outbound; and a piston slidably placed in the controller body. A receiving passage is isolated from any of the input and output passages and the input, output and exhaust ports in each of an open, closed and exhaust operating condition of the controller. The receiving passage connects in fluid form with a chamber upstream of the piston and with a pressurization chamber of the exhaust valve. An inlet seat valve slidably positioned is adapted to isolate the outlet passage from the inlet passage in a closed position of the inlet seat valve. The inlet seat valve is normally referred to the closed position of the inlet seat valve. An exhaust seat valve slidably positioned is normally held in a closed position of the exhaust seat valve by the pressurized fluid in the pressurization chamber of the exhaust valve. The exhaust seat valve is adapted to isolate the exhaust passage of the exhaust port in the closed position of the exhaust seat valve.

In accordance with other embodiments, a proportional pressure controller includes a controller assembly having open, closed / achieved and exhaust pressure controller positions. The controller set also includes: a body that has input, output and exhaust ports and a common exit / escape passage; a filling valve in communication with a pressurized fluid in the inlet port; a discharge valve in communication with the pressurized fluid in a discharge passage of the filling valve; and a piston slidably positioned in the body, in communication with a piston pressurization chamber and displaced in response to the pressurized fluid entering the piston pressurization chamber. An inlet seat valve that contacts the piston is slidably placed in the body. The inlet seat valve is normally referred to a closed position of the inlet seat valve in the closed controller position. The seat valve

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Inlet is mobile by moving the piston to an open position of the inlet seat valve that defines the open position of the controller. An exhaust seat valve is slidably placed in the body and is maintained in a closed position of the exhaust seat valve by the pressure of the fluid directed through the filling valve acting on an end face of the exhaust seat valve. The

The fluid pressure creates a greater force than the force due to the pressure in the common exhaust passage of the body acting on an opposite side of the exhaust seat valve. The exhaust seat valve isolates the pressurized fluid from the exhaust port when it is in the closed position.

According to additional embodiments, a proportional pressure controller includes a controller assembly that has open, closed / achieved pressure and exhaust controller conditions. The controller assembly 10 also includes: a body having inlet, outlet and exhaust ports and a common escape / exit passage; and a valve system adapted to control the flow of a pressurized fluid. An inlet seat valve is slidably placed in the body and is normally referred to a closed position of the inlet seat valve that defines the closed condition of the controller. The inlet seat valve is movable to an open position of the inlet seat valve that defines the open condition of the controller by means of the pressurized fluid directed through the valve system. An exhaust seat valve is slidably placed in the body and held in a closed position of the exhaust seat valve by the fluid pressure directed through the valve system in an exhaust valve pressurization chamber. . An outflow passage is in communication with the pressurized fluid from the inlet port, when the inlet seat valve is moved to the open position of the inlet seat valve. The outlet flow passage 20 communicates with the outlet port and the common exhaust / outlet passage is normally isolated from the exhaust port, when the exhaust seat valve is in the closed position of the exhaust seat valve. A filling inlet passage provides fluid communication between the inlet passage and the valve system. The filling inlet passage is isolated from each of the outflow passage, the common exhaust / outlet passage and the outlet and exhaust ports in all controller operating conditions. The filling entry passage is

25 communicates with and continuously pressures through the pressurized fluid in the inlet passage.

Additional areas of applicability will be apparent from the description provided here. The description and specific examples in this summary are intended for illustration purposes only and are not intended to limit the scope of the present disclosure.

The drawings described herein are for illustrative purposes only of selected embodiments and not all 30 possible implementations, and are not intended to limit the scope of the present disclosure.

Figure 1 is a left front perspective view of a proportional pressure controller of the present disclosure;

Figure 2 is a side elevational view of the proportional pressure controller of Figure 1;

Figure 3 is a front elevational view in cross section taken in section 3 of Figure 2;

Figure 4 is a front elevational view in cross section similar to Figure 3, showing the inlet seat valve of the proportional pressure controller in an open position;

Figure 5 is a front elevation view in cross-section similar to Figure 3, showing the exhaust seat valve of the proportional pressure controller in an open position;

Figure 6 is a front elevational view in cross section similar to Figure 3 of another embodiment of a proportional pressure controller of the present disclosure;

Figure 7 is a front elevational view in cross section similar to Figure 3 of another embodiment of a proportional pressure controller of the present disclosure;

Figure 8 is a front elevational view in cross section similar to Figure 3 of another embodiment of a proportional pressure controller of the present disclosure;

Figure 9 is a front elevational view in cross section similar to Figure 3 of another embodiment of a proportional pressure controller of the present disclosure; Y

Figure 10 is a schematic representation of the proportional pressure controller of Figure 1.

The corresponding reference numbers indicate corresponding parts through the various views of the drawings.

50 Example embodiments will now be described more fully with reference to the accompanying drawings.

Example embodiments are provided so that this disclosure is complete and fully describes the scope to those skilled in the art. Numerous specific details are indicated as examples of specific components, devices and procedures to provide a complete understanding of the

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embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details should not be used, that exemplary embodiments can be made in many different ways and should not be considered to limit the scope of the disclosure. In some exemplary embodiments, well known processes, well known device structures and well known technologies are not described in detail.

The terminology used herein is for the purpose of describing particular example embodiments only and is not intended to be limiting. As used herein, the singular forms "un", "una" and "el / la" may also be intended to include the plural forms; unless the context clearly indicates otherwise. The terms "comprises", "comprising", "including" and "having" are inclusive and, therefore, specify the presence of indicated characteristics, integers, stages, operations, elements and / or components, but does not prevent the presence or addition of one or more other characteristics, integers, stages, operations, elements, components and / or groups thereof. The steps of procedure, processes and operations described in this document should not be considered as necessarily requiring their realization in the particular order described or illustrated, unless specifically identified as an order of realization. It should also be understood that additional or alternative steps may be employed.

When an element or layer is indicated to be "over", "coupled with", "connected with" or "interconnected with", another element or layer, may be directly in, coupled, connected or interconnected to the other element or layer, or there may be intermediate elements or layers. In contrast, when it is indicated that an element is "directly in", "directly coupled with", "directly connected with" or "directly interconnected with" another element

or layer, there may be no intermediate elements or layers present. Other words used to describe the relationship between elements should be interpreted similarly (for example "between" with respect to "directly between", "adjacent" with respect to "directly adjacent", etc.). As used herein, the term "and / or" includes any and all combinations of one or more of the associated elements cited.

Although the terms first, second and third, etc., may be used herein to describe various elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms These terms can only be used to distinguish an element, component, region, layer or section from another region, layer or section. Terms such as "first", "second" and other numerical terms when used herein do not imply a sequence or order, unless clearly indicated by context. In this way, a first element, component, region, layer or section described below can be called a second element, component, region, layer

or section, without departing from the teachings of the example embodiments.

Spatially relative terms such as "interior", "exterior", "below", "inferior", "minor", "above", "superior" and the like, may be used herein for ease of description, to describe an element or relationship of characteristics with another or other elements or characteristics, as illustrated in the figures. Spatially relative terms can be intended to cover different orientations of the device in use or operation, in addition to the orientation illustrated in the figures. For example, if the device in the figures is rotated, the elements described as "below" or "below" other elements or features will then be oriented "over" the other elements or features. In this way, the example term "below" can cover an orientation above and below. The device may be oriented in another way (rotated 90 degrees or in other orientations) and the spatial relative descriptors employed herein will be interpreted accordingly.

With reference to Figure 1, a proportional pressure controller 10 includes a body 12 having a first end cap 14 at a first end and a second end cap 16 at an opposite end. The first and second end caps 14, 16 can be releasably attached or fixedly connected to the body 12. A separator element 18 can also be included with the body 12, the purpose of which will be described with reference to Figure 3. An operator of the controller 20 can be connected such as by clamping or fixed connection to a portion 22 of the central body. The body 12 may further include a portion 24 of the input body connected between the portion of the central body 22 and the spacer 18, with the spacer 18 positioned between the portion 24 of the inlet body and the second end cap 16. The body 12 may also include an exhaust body portion 26 placed between the portion 22 of the central body and the first end cap 14.

With reference to Figure 2, the proportional pressure controller 10 can be provided in the form of a generally rectangular shaped block body, such that multiple of the proportional pressure controllers 10 can be arranged in a configuration next to each other. This geometry also promotes the use of the proportional pressure controller 10 in a manifold configuration.

With reference to Figure 3, according to various embodiments, portions 24, 26 of the inlet and exhaust body are releasably connected and sealed to portion 22 of the central body. The proportional pressure controller 10 may each include an inlet port 28, an outlet port 30, and an exhaust port 32, each created in the portion 22 of the central body. A pressurized fluid, such as pressurized air, can be discharged from the proportional pressure controller 10 through the outlet port 30 through an outlet flow passage 34. The flow to the outflow passage 34 can be isolated using an inlet seat valve 36. The inlet seat valve 36 normally sits against an inlet valve seat 38 and is maintained.

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in the seated position shown with the assistance of the force of a thrust element 40, such as a compression spring, which defines a closed condition of the controller, in which fluid flow is not discharged through the outlet port or Exhaust 30, 32. The thrust element 40 may be held in position by contact with an end wall 41 of the portion 24 of the inlet body, and in the opposite manner when partially received in a valve cavity 42 of the seat valve. inlet 36. The inlet seat valve 36 can slide axially in each of a closing direction "A" of the inlet valve extending the thrust element 40 and an opening direction "B" of the opposite inlet valve which compresses the thrust element 40.

Directed in the opposite direction from the valve cavity 42 is a stem 43 of the inlet valve that extends integrally and axially from the inlet seat valve 36 and is coaxially aligned with the thrust element 40. A free end of the stem 43 of the inlet valve contacts a piston 44. The stem 43 of the inlet valve is slidably positioned through a first limiting wall 45 before contacting the piston 44 to help control an axial alignment of the valve of inlet seat 36, to promote a perimeter seal of a seat ring 46 with the seat 38 of the inlet valve in the closed position. The pressurized fluid can flow freely through the first limiting wall 45 through at least one hole 47 and / or through the perforation that allows the passage 43 of the inlet valve. The size and quantity of the at least one hole 47 control the time required for the pressure in the outflow passage 34 to act on the piston 44 (on the left side as seen in Figure 3) and, therefore , the speed of the piston movement. The pressure acting through the at least one hole 47 creates a pressure pushing force that acts to move the piston 44 to the closed position. The piston 44 can be provided with at least one, and according to several embodiments, a plurality of elastic U-cup seals 48, which are individually housed in individual seal grooves 49 created around a perimeter of the piston 44. U-cup seals 48 provide a fluid pressure seal around the piston 44 when the piston 44 slides axially into a cylinder cavity 50.

The piston 44 moves coaxially with the inlet seat valve 36 in the closing direction "A" of the inlet valve or in the opening direction "B" of the inlet valve. The first limiting wall 45 defines a first limit (a limit without pressure) and the piston 44 defines a second limit (a pressure limit) of a cylinder cavity 50 that slidably receives the piston 44. The piston 44 can move in the opening direction "B" of the inlet valve until one end 51 of the piston 44 contacts the first limiting wall 45 (on one side facing the right of the first limiting wall 45, as seen in the Figure 3) with the first limitation wall 45 that is fixed in position. The piston 44 is retained within the cylinder cavity 50 by contact with the first limiting wall 45 by the previously described pressure thrust force created by the pressurized fluid flowing freely through the holes 47. The piston 44 also it is retained within the cylinder cavity 50 by contact at an opposite end of the cylinder cavity 50 with portions of the separator element 18 extending radially beyond a cylindrical wall of the cylinder cavity 50, as shown.

An elastic sealing element 52, such as an O-ring, can be placed inside a circumferential groove or groove 53 created externally with respect to a perimeter of the inlet seat valve 36. The elastic sealing element 52 provides a relief capacity for the pressurized fluid in the valve cavity 42 which will also be described with reference to Figure 5.

The proportional pressure controller 10 can be operated using each of a fill or inlet valve 54 and a discharge valve 56 that can be releasably connected to the central body portion 22 within the controller operator 20. A pressurized fluid , such as pressurized air, housed in the inlet port 28 is filtered or purified in a common manner. The fluid that can flow turns the proportional pressure controller 10 through the outlet port 30 and the outlet flow passage 34 is potentially contaminated fluid. According to several embodiments, the fill and discharge valves 54, 56 are isolated from the potentially contaminated fluid, such that only the filtered air or the fluid received through the inlet port 28 flows through the fill valve 54 or the discharge valve 56. An inlet flow passage 58 communicates between the inlet port 28 and the outlet flow passage 34 and is isolated in the outlet flow passage 34 by the inlet seat valve 36, which can close normally. An air supply port 60 communicates with the inlet flow passage 58 and through a filling inlet passage 62 that is isolated from the outlet flow passage 34, which provides pressurized fluid or air to the filling valve 54 A valve discharge passage 64 provides a route for the air flowing through the filling valve 54 to address an inlet of the discharge valve 56 and a plurality of different passages.

One of these passages includes a pressurization passage 66 of the piston that directs air or fluid from the discharge passage 64 of the valve to a pressurization chamber 68 of the piston created in the second end cap 16. The pressurized air or fluid in the pressurization chamber 68 of the piston generates a force acting on an end face 70 of the piston 44. A surface area of the end face 70 of the piston is larger than a surface area of the inlet seat valve 36 in contact with the seat 38 of the inlet valve, therefore when the filling valve 54 opens or continues to open further, the net force created by the pressurized fluid acting on the end face 70 of the piston causes the piston 44 move initially or move further in the opening direction "B" of the inlet valve and away from the seat 38 of the inlet valve. This initially opens

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or allows an additional increased flow in a flow passage between the inlet flow passage 58 and the output flow passage 34, to allow the pressurized fluid to exit the proportional pressure controller 10 at the outlet port 30, defining an open condition of the controller, in which the fluid from the inlet flow passage 58 is discharged through the outlet port 30 (no flow through the exhaust port 32). This operation will be explained more fully with reference to Figure 4. The proportional pressure controller 10 can initiate the flow of pressurized fluid between the inlet port 28 and the outlet port 30 if there is no flow present in the outlet port 30 , or the proportional pressure controller 10 can maintain, increase or decrease the pressure of an existing flow of the pressurized fluid between the inlet port 28 and the outlet port 30 in those situations where a continuous regulated fluid flow is required. under pressure

A portion of the pressurized fluid discharged through the filling valve 54 through the valve discharge passage 64, is directed by a pressurization passage 72 of the exhaust valve created in a connection wall 74 of the portion 22 of the central body inside a pressurization chamber 76 of the exhaust valve. When the filling valve 54 opens and the discharge valve 56 closes, the air or pressurized fluid received in the pressurization chamber 76 of the exhaust valve, by means of the pressurization passage 72 of the exhaust valve, acts against an end face 78 of the exhaust valve of an exhaust seat valve 80, to retain the exhaust seat valve 80 in a seated position shown.

The exhaust seat valve 80 includes a seat ring 83 for the exhaust seat valve, which contacts a seat 84 of the exhaust valve in the seated position of the exhaust seat valve 80. When the exhaust valve Exhaust seat 80 is in the seated position shown in Figure 3, the pressurized fluid flowing from the outlet flow passage 34 through the outlet port 30, which also enters a common exhaust / outlet passage 86, It is isolated from the exhaust port 32 to prevent the outflow of the pressurized flow of the exhaust port 32 through an exhaust flow passage 88.

The exhaust seat valve 80 includes a rod 90 of the axially extending, integrally connected exhaust valve that is slidably received in a receiving passage 92 of the stem of a receiving element 94 of the stem. The receiving element 94 of the rod is placed between a second limiting wall 96 and the first end cap 14. Similar to the first limiting wall 45, the pressurized fluid can flow freely through the second limiting wall 96 by at least one hole 97. The size and amount of the hole (s) 97 control the speed at which the pressure is balanced through the second limiting wall 96. A passage 98 of the discharge valve is provided on one side. of discharge of the discharge valve 56, which communicates through an exhaust port 100 of the discharge valve of the portion 22 of the central body with the exhaust flow passage 88. It should be noted that the outlet passage 98 of the valve Discharge is isolated and, therefore, does not provide fluid communication with the pressurization passage 72 of the exhaust valve, the discharge passage 64 of the valve or the pressurization passage 66 of the piston.

It should also be noted that each of the discharge passage 64 of the valve, the pressurization passage 66 of the piston, the pressurization passage 72 of the exhaust valve and the passage 98 of the discharge valve are isolated from the fluid pressure in the outflow passage 34 or the common exhaust / outlet passage 86 when the fill valve 54 is open. These flow passages, therefore, allow the communication of the filtered or fluid air from the inlet port 28 to communicate through the fill or discharge valve 54, 56 without exposing the fill or discharge valves 54, 56 to the potentially contaminated fluid of the outlet port 30.

The proportional pressure controller 10 can also include a circuit board 101 placed inside the operator of the controller 20 that is in electrical communication with both fill and discharge valves 54, 56. The signals received on the circuit board 101 to place the control of the fill or discharge valve 54, 56, are received by a wiring harness 102 in the operator of the controller 20, which is sealed using a connecting plug 104. A control system 106 placed remotely performs the calculation of functions and sends the command signals to the circuit board 101 that controls either or both of the fill and / or discharge valves 54, 56, to control a system pressure at the output port 30. Control signals from and to the proportional pressure controller 10 and the control system 106 communicate using a control signal interface 108. The control signal interface 108 may be a connection With physical wiring (for example, wiring harness), a wireless connection (for example radio or infrared) or the like. The closed condition of the controller shown in Figure 3 for the proportional pressure controller 10 is provided when both fill and discharge valves 54, 56 are closed, with the inlet seat valve 36 seated against the inlet seat 38 of the inlet valve. , and the discharge seat valve 80 seated against the seat 84 of the exhaust valve.

The configuration shown in Figure 3 is not limiting. For example, although the inlet seat valve 36 and the exhaust valve seat valve 80 are illustrated in an opposite configuration, these seat valves can be placed in any configuration at the discretion of the manufacturer. Alternative configurations can provide the seat valves in a parallel arrangement side by side. The seat valves can also be oriented such that both seat valves settle in the same axial direction and become detached or released in the same opposite axial direction. The configuration shown in Figure 3, therefore, is exemplary of a possible configuration. The configuration shown in Figure 3 indicates a closed configuration, with no inlet pressure in communication with the outlet port 30, or a pressure condition achieved that

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occurs when a desired pressure is reached at the outlet port 30, but no additional flow is required, at least temporarily, through the outlet port 30. Figure 4 can also illustrate the pressure condition achieved, which occurs when a steady state flow of fluid is achieved at a desired pressure through the outlet port 30. The pressure condition achieved can occur in any position of the inlet seat valve 36 relative to the inlet valve seat 38 between, and including, a seated and fully open position.

Referring to Figure 4, the open condition of the controller or pressurization configuration of the proportional pressure controller 10 is illustrated. In the open condition, a signal is received to open the filling valve 54, with the discharge valve 56 being retains in a closed position. When the fill valve 54 is opened, a portion of the air or fluid in the inlet port 28 flows through the fill valve 54 through the pilot air supply port 60 and the inlet-fill passage 62. This air flow leaves the filling valve 54 to the discharge passage 64 of the valve. The fluid pressure in the discharge passage 64 of the valve is detected by a pressure sensor, such as a first pressure signaling device 110, which according to various embodiments can be a pressure transducer. Pressurized fluid in the discharge passage 64 of the valve is partly directed through the pressurization passage 66 of the piston in the pressurization chamber 68 of the piston to force the piston 44 to slide in the opening direction "B" of the inlet valve acting against the stem 43 of the inlet valve to push the inlet seat valve 36 away from the inlet seat 38 of the inlet valve, compressing the thrust element 40. This opening movement of the seat valve inlet 36 creates an inlet flow ring 111 that allows the pressurized fluid in the inlet flow passage 58 to flow through the inlet flow ring 111 into the outlet flow passage 34, and from there as shown by means of the various flow arrows, outside the proportional pressure controller 10 through the outlet port 30. A first hole 112 may be provided to allow fluid on the side of the cavity Valve ad 42 of the inlet seat valve 36 moves to the outlet flow passage 34 at a controlled speed, allowing the sliding speed and, therefore, the timing of the opening of the inlet seat valve 36 is predetermined. The pressurized fluid exiting the outlet port 30 can be directed to a pressure operated device 114, such as a piston operator or similar drive. The first orifice 112 also allows the pressure in the outlet flow passage 34 to act on the seat side of the seat valve 36 creating an additional thrust force towards the closed position.

The first limiting wall 45 can also function as a contact surface that stops the sliding movement of the piston 44 in the opening direction "B" of the inlet valve. A duration of time in which the inlet seat valve 36 is in the open position can be used together with the pressure detected by the first pressure signaling device 110 to proportionally control the pressure in the pressure actuating device 114. As the First pressure signaling device 110 is also placed within the valve discharge passage 64, the first pressure signaling device 110 is also isolated from potential contaminants that may be present at the outlet port 30. This reduces the possibility that the contaminants affect the pressure signal of the first pressure signaling device

110. As previously indicated, when the pressurized fluid is discharged through the outlet port 30 and when the fill valve 54 is in the open position, the pressurized fluid from the valve discharge passage 64 is received by the passage pressurization of the exhaust valve 72 in the pressurization chamber 76 of the exhaust valve, to retain the exhaust seat valve 80 in its seated position by forcing the exhaust seat valve 80 in the closing direction "C" of the exhaust valve.

With reference to Figure 5, when a desired pressure is reached in the pressure operated device 114 as detected by the first pressure signaling device 110, the filling valve 54 is directed to close and the discharge valve 56 can be directed to open The discharge valve 56 will also open if the pressure reaches a predetermined (high) pressure or the command signal is given to reduce the pressure. When the filling valve 54 is in the closed position, the pressure fluid in the filling inlet passage 62 is isolated from the discharge passage 64 of the valve. When the discharge valve 56 is opened, the pressurization passage 72 of the exhaust valve is vented to discharge the flow passage 88 through the discharge passage 64 of the valve and the outlet passage 98 of the discharge valve. The residual fluid pressure in the outlet port 30 and in the common outlet / exhaust passage 86, therefore, exceeds the pressure in the pressurization passage 72 of the exhaust valve, forcing the exhaust seat valve 80 to move in the opening direction "D" of the exhaust valve. At this same time, the air or pressurized fluid in the pressurization passage 66 of the piston also vents the exhaust flow passage 88 through the discharge passage 64 of the valve and the outlet passage 98 of the discharge valve. This imbalances the forces acting on the inlet seat valve 36 of the piston 44, such that the thrust force of the thrust element 40 plus the fluid pressure in the outflow passage 34 combine to return the valve. of inlet seat 36 in the closing direction "A" of the inlet valve to seat the inlet seat valve 36 against the seat 38 of the inlet valve. The at least one orifice 47 provided through the first limitation wall 45 allows the fluid pressure to be equalized through the first limitation wall 45, increasing the sliding speed of the piston 44 when the valve is closed. inlet seat 36. The inlet seat valve 36 may also be in the closed condition if the desired pressure is reached at the outlet port 30 and is static.

When the exhaust seat valve 80 moves in the opening direction "D" of the exhaust valve, an exhaust flow ring 116 is opened to allow flow in the direction of the multiple flow arrows shown

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from the common exhaust / outlet passage 86 to the exhaust flow ring 116, within the exhaust flow passage 88, and exiting through the exhaust port 32. The signal to open the discharge valve 56 is also received when the pressure on the pressure operated device 114 exceeds the desired pressure setting. When the desired pressure setting is exceeded, it is advantageous to discharge the fluid with a higher pressure through the exhaust port 32 as quickly as possible. The pressure-balanced exhaust seat valve 80, therefore, opens, allowing rapid depressurization through the common exhaust / outlet passage 86, the exhaust flow ring 116, the exhaust flow passage 88 and the exhaust port 32. With the discharge valve 56 open, the outlet passage 98 of the discharge valve depressurizes the discharge passage 64 of the valve, the pressurization passage 66 of the piston, the pressurization chamber 68 of the piston and the pressurization passage 72 of the exhaust valve is also depressurized by the exhaust port 32.

With reference to Figures 5 and 3, when the discharge valve 56 receives a signal to close when the pressure in the discharge passage of the valve 64, detected by the first pressure signaling device 110 reaches the desired pressure, the valve of exhaust seat 80 will remain in the open position until the pressure in the pressurization chamber 76 of the valve exceeds the pressure in the common exhaust / outlet passage

86. The fluid pressure in the pressurization passage 72 of the exhaust valve forces the exhaust seat valve 80 in the closed direction of the exhaust valve "C", against the seat 84 of the exhaust valve until the Pressure in the common outlet / exhaust passage 86 exceeds the pressure in the pressurization chamber 76 of the valve.

With reference to Figure 6, according to additional embodiments, a proportional pressure control 120 is modified from the proportional pressure controller 10 to provide a different type of fill valve 122 and discharge valve 124. For example, the pressure valve fill 122 and discharge valve 124 may be hydraulically operated, solenoid operated or air operated valves, which may provide different operating characteristics for proportional pressure controller 120. Proportional pressure controller 120 may also include a second pressure sensor. pressure, such as a second pressure signaling device 126, such as a pressure transducer placed in the output flow passage 34 '. The addition of the second pressure signaling device 126 may provide a highlighted / additional sensitivity pressure detection signal at the output port 30 '. Using the pressure or output signals received from the first pressure signaling device 110 and the second pressure signaling device 126, a finer position and / or timing of opening / closing timing of the controller valve elements can be provided of proportional pressure 120 to mitigate the failure to reach or exceed the desired pressure at the outlet port 30 '. The remaining components of the proportional pressure controller 120 are substantially the same as those described with reference to the proportional pressure controller 10 of Figure 3. The failure to achieve the desired pressure at the outlet port of the known proportional pressure control devices it can result in a rapid opening / closing operation of the control valves, known as "motor navigation", when the controller attempts to correct the desired pressure by moving the solenoid operated valves in response to a pressure signal. The use of first and second pressure signaling devices 110 ', 126 may provide a differential pressure between the inlet pressure, detected by the first pressure signaling device 110', and the output port pressure 30 'detected by the second pressure signaling device 126, which together provide a real-time difference between the desired output pressure and the pilot pressure. Together with the quick-acting seat valves (which respond to pressure differences and do not require a control signal) the proportional pressure controller 120 can help mitigate the possibility of motor navigation.

With reference to Figure 7 and again to Figure 3, in accordance with other embodiments, a proportional pressure controller 128 may include a portion 130 of the central body that is modified from portion 22 of the central body and may include a portion 131 of the inner body that is modified from the portion 24 of the inlet body shown in Fig. 3. The inlet seat valve 36 'is provided with a U-shaped sealing element 132 and is slidably positioned in a Pressure chamber 134 of the inlet seat valve. The pressurized fluid leaving the pressure chamber 134 of the inlet seat valve, when the inlet seat valve 36 'moves in the opening direction "B" of the inlet valve, is discharged by a first orifice 112 'which can be modified at the discretion of the manufacturer to change the flow characteristics of the fluid exiting the pressure chamber 134 of the inlet seat valve, thereby affecting the operating speed of the inlet seat valve 36 '. An outlet flow passage orifice 136 created in the portion 130 of the central body can also be used to control the flow rate of fluid from the outlet flow passage 34 'to the outlet port 30 ". The combination of the first hole 112 'and the orifice of the outlet flow passage 136 can be used to increase or decrease the flow rate of the pressurized fluid through the outlet port 30 ". In addition, by selecting the type of valve used for the fill valve 122 and the discharge valve 124 in the proportional pressure controller 128, a type of valve that is less susceptible to operational problems of the contaminants present in the outlet port 30 ", can reduce the need for a second U-cup seal on piston 44 ', so that only the single U-cup seal 48' can be used. This can also reduce the friction associated with the sliding movement of the piston 44 'to further improve the operating speed of the inlet seat valve 36'.

With reference to Figure 8 and again to Figure 3, in accordance with still further embodiments, a proportional pressure controller 138 may include a portion 140 of the modified central body relative to the portion of the

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central body The proportional pressure controller 138 may include a 3-way valve 142 employed in place of the fill and discharge valves of the previous embodiments. A pilot air outlet passage 144 that communicates through the 3-way valve 142, can similarly direct the pressurized fluid through the pressurization passage 66 'of the piston to the pressurization chamber 68 of the piston and piston 44. The pressurized fluid of the pilot air outlet passage 144 can also be directed by a pressurization passage 146 of the exhaust valve into the pressurization chamber 76 'of the exhaust valve, to fully seat the exhaust seat valve 80 '. A separate discharge pressure passage 148 that communicates with the 3-way valve 142 can also vent the pressurized fluid through the exhaust port of the discharge valve 100 'to the exhaust port 32'. A fluid or pilot air inlet passage 150 may be created in portion 140 of the central body, to eliminate the need for a separate internal passage that provides pilot air to the 3-way valve 142. The operation of the proportional pressure controller 138 of Another way is similar to the proportional pressure controllers previously described herein.

With reference to Figure 9 and again to Figures 3 and 6 to 8, the operating valves, such as the fill and discharge valves or the 3-way valves previously described for the other embodiments of proportional pressure controllers of the This disclosure may be eliminated by the design shown for a proportional pressure controller 152. The proportional pressure controller 152 includes a central body portion 154 also modified from the portion 22 of the central body shown and described with reference to Figure 3 to include only a pilot air reception passage 156 that communicates via a pilot air outlet passage 158 to a pressurization passage 160 of the piston and an exhaust pressurization passage 162. The proportional pressure controller 152 removes all valves actuator mounted by the controller and retains only the seat valves of the previ designs Amente described. This allows the space envelope of the proportional pressure controller 152 to be minimized and provides complete remote control of the proportional pressure controller 152.

Referring to FIG. 10, the proportional pressure controller 10 can provide the first pressure signaling device 110 within the outlet discharge passage 64 of the valve to isolate the first pressure signaling device 110 from the contaminated fluid in the passage output flow 34, which helps mitigate against contamination that affects pressure signal 164 or the timing of pressure signal generation

164. A signal for opening the filling valve 54 provides a flow of pressurized fluid in the filling inlet passage 62 to the inlet seating valve 36 by the pressurizing passage 66 of the piston and also provides a flow of fluid to pressure to discharge the end face 78 of the exhaust seat valve 80 via the pressurization passage of the exhaust valve 72. The pressurized fluid discharged from the filling valve 56 is immediately discharged through a discharge port 166 of the filling valve, which communicates with the discharge passage 64 of the valve and with the inlet port of the discharge valve 168. The pressurized fluid in the inlet port 168 of the discharge valve can be blocked by the discharge valve 56 that enters the outlet passage 98 of the discharge valve and is discharged through the exhaust port 32, unless the discharge valve 56 is closed.

The proportional pressure controllers of the present disclosure offer several advantages. By eliminating the solenoid actuators associated with the main flow valves of the controller and replacing the valves with seat valves, small and lower power consumption pilot valves are used, in the form of fill and discharge valves to provide a pressure drive to open or close the seat valves. This reduces the cost and operating energy required for the controller. The use of passages created in the controller body to transfer pressurized fluid to drive the seat valves that are isolated from the main seat valve flow paths, prevents potentially contaminated fluid at the controller outlet from flowing back into pilot valves, which could inhibit their operation. One of the passages can be used to simultaneously provide pressure to open one of the seat valves while keeping the second seat valve in a closed position. By placing a pressure sensing device in one of the insulated passages, the pressure sensing device is also isolated from contaminants, to improve the accuracy of the pressure signal of the device. In addition, the fill and discharge valves can be provided in the form of multiple valves, including solenoid operated valves, hydraulically operated valves and a 3-way valve that replaces the filling and discharge valves.

The above description of the embodiments has been provided for purposes of illustration and description. It is not intended to be exhaustive or to limit the invention. Individual elements or features of a particular embodiment in general are not limited to that particular embodiment, but when applicable, are interchangeable and can be used in a selected embodiment, even if not specifically illustrated or described. The same can also be varied in many ways. These variations should not be considered as a separation of the invention, and all these modifications are intended to be included within the scope of the invention.

Claims (15)

E10193281 10-12-2014 1. A proportional pressure controller (10), comprising: a controller set that includes: a body that has ports of entry (28), exit (30) and exhaust (32); 5 a filling valve (54), in communication with a pressurized fluid in the inlet port; a discharge valve (56) in communication with the pressurized fluid in a discharge passage of the filling valve; an inlet seat valve (36) and an exhaust seat valve (80); an outlet flow passage (34) in communication with the pressurized fluid when the valve 10 inlet seat (36) moves to an open position of the inlet seat valve, the outflow passage (34) communicating with the outlet port (30) and a common exhaust / outlet passage (86) normally isolated from the exhaust port when the exhaust seat valve is in a closed position of the exhaust seat valve; Y an inlet and fill passage (62) that provides fluid communication between a passage of 15 inlet flow (58) and filling valve (54), and isolated from each other, the outlet flow passage (34), the common exhaust / outlet passage (86) and the outlet and exhaust ports in all operating conditions of the controller, the inlet and filling passage (62) communicating with the inlet passage (58) and being continuously pressurized by the pressurized fluid in the inlet passage; and characterized in that it includes a first pressure signaling device (110) 20 adapted to emit a detected pressure signal, placed in the discharge passage downstream of the filling valve (54) to isolate the fluid pressure signaling device at the outlet port. 2. A proportional pressure controller (10) according to claim 1, which also includes: a piston (44) in fluid communication with the filling valve (54) and adapted to move the valve 25 inlet seat (36) from a closed position to the open position of the inlet seat valve; a chamber (68) upstream of the piston; Y a valve discharge passage (64) in communication with the pressurized fluid of the filling valve (54), which provides the pressurized fluid to each of the pressurization chamber (78) of the valve (80) of the 30 chamber, the valve discharge passage (64) of each one being isolated, the outlet flow passage (34), the common exhaust / outlet passage (86), and the outlet port (30) in all the operating conditions of the controller. 3. A proportional pressure controller (10) according to claim 1 or 2, wherein the inlet seat valve (36) is slidably disposed in the body and is normally pressed to a closed position 35 of the inlet seat valve defining a closed condition of the controller, the inlet seat valve (36) being displaced to the open position of the inlet seat valve (36) by the pressurized fluid directed through the filling valve (54) resulting from the opening of the filling valve, defining an open condition of the controller; and wherein the exhaust seat valve (80) is slidably disposed in the body and is held in the closed position of the exhaust seat valve (80) by pressure 40 of the fluid directed through the filling valve (54), the exhaust seat valve (80) isolating the pressurized fluid from the exhaust port (32). 4. A proportional pressure controller (10) according to any preceding claim, wherein when the fill valve (54) is closed and the discharge valve (56) is open, a discharge valve outlet passage ( 98) in fluid communication with the exhaust port (32) allows the valve discharge passage 45 (64) is depressurized through the exhaust port and allows the exhaust valve (80) to open by venting the outflow passage (34) and the common exhaust / outlet passage (86) through the exhaust port. escape. 5. A proportional pressure controller (10) according to claim 1, which also includes: a piston (44) slidably disposed in the body; a receiving passage (92) isolated from any of the input and output flow passages and from the 50 inlet (28), outlet (30) and exhaust (32) ports in each open, closed and exhaust operating condition of the controller, connecting the receiving passage (92) fluidly with a chamber upstream of the piston and with a chamber pressurization (76) of the exhaust valve; 10 5 10 fifteen twenty 25 30 35 40 Four. Five fifty E10193281 10-12-2014 the inlet seat valve (36) being adapted to isolate the outlet flow passage (34) from the inlet flow passage (58) in a closed position of the inlet seat valve, the inlet seat valve being (36) normally pressed to the closed position of the inlet seat valve; Y the exhaust seat valve (80) being normally kept in a closed position of the exhaust seat valve by means of the pressurized fluid in the pressurization chamber (76) of the exhaust valve, the exhaust seat valve being adapted ( 80) to isolate the exhaust flow passage from the exhaust port (32) in the closed position of the exhaust seat valve.

6.

 A proportional pressure controller (10) according to claim 5, which also includes a limiting wall (45) positioned between the piston (44) and the inlet seat valve (36) having at least one opening (47 ) which allows fluid flow through the limitation wall (45).

7.

A proportional pressure controller (10) according to claim 5 or 6, wherein the inlet seat valve (36) includes:

a valve cavity (50) that receives a pushing element (40) that operates to normally push the inlet seat valve (36) in a closed direction of the inlet valve; and a seat ring (46) adapted to seal a valve seat.

8.

A proportional pressure controller (10) according to any one of claims 5 to 7, wherein the inlet seat valve is movable to the open position of the inlet seat valve when the pressurized fluid is directed through from the receiving passage (66) to the piston chamber (68), the pressurized fluid acting on a surface area (70) of the piston that is larger than a surface area of the inlet seat valve (36), creating a force that operates to move the piston (44) that pushes the inlet seat valve

(36) to the open position of the inlet seat valve.

9.

 A proportional pressure controller (10) according to any one of claims 5 to 8, wherein the inlet seat valve (36) includes a rod (43) extending axially from the inlet seat valve (36 ) adapted to contact the piston (44), in which the pressurization of the piston chamber induces the movement of the piston that contacts the rod (43), to induce the sliding movement of the inlet seat valve (36) to the open position of the inlet seat valve.

10.

 A proportional pressure controller (10) according to claim 1, wherein the inlet seat valve (36) is slidably placed in a pressure chamber, the pressure chamber being in fluid communication with the passage outflow (34) through an orifice (112) sized to control an operating speed of the inlet seat valve.

eleven.

 A proportional pressure controller (10) according to claim 2, wherein:

the controller includes an inlet (24), exhaust (26) and central (22) body portions, the inlet and exhaust body portions being connected releasably and tightly to the central body portion; the ports of entry, exit and escape are created in the central body portion; the central body portion receives the inlet valve (36) and the exhaust valve (80); the inlet seat valve (36) and the piston (44) are slidably placed in the inlet body portion (24); Y The exhaust seat valve (80) is slidably positioned in the exhaust body portion (26). 12. A proportional pressure controller (10) according to claim 2, wherein the filling valve (54) in communication with the inlet and fill passage (62), operates to isolate the pressurized fluid from the inlet (36) and exhaust (80) seat valves when the fill valve is in a closed position, and when open it allows the flow of the pressurized fluid to act on an end face of the piston and an end face of the exhaust valve. 13. A proportional pressure controller (10) according to claim 12, wherein; the discharge valve (56), when open, decreases a pressure of the pressurized fluid acting on the end face (70) of the piston and the end face (78) of the exhaust valve; Y The discharge valves (56) and the filling valve (54) each comprise a solenoid operated valve. eleven E10193281 10-12-2014 14. A proportional pressure controller (10) according to any preceding claim, which also includes: a control system adapted to receive the pressure signal detected from the first pressure signaling device (110) and control the filling (54) and discharge valves (56); Y 5 a second pressure signaling device (126) placed in an outflow passage (34) of the outlet port (30) adapted to emit a second detected pressure signal that is received by the control system to fine tune the control of the filling (54) and discharge (56) valves. 15. A proportional pressure controller (10) according to any preceding claim, wherein fill and discharge valves (54) are air-operated fill and discharge valves, which has the fill valve 10 in communication with the inlet passage (62) of the fill valve. 12